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EP1764574A1 - Wärmetauscher - Google Patents

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Publication number
EP1764574A1
EP1764574A1 EP06018890A EP06018890A EP1764574A1 EP 1764574 A1 EP1764574 A1 EP 1764574A1 EP 06018890 A EP06018890 A EP 06018890A EP 06018890 A EP06018890 A EP 06018890A EP 1764574 A1 EP1764574 A1 EP 1764574A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
coolant
guide passage
exchanger according
intake guide
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP06018890A
Other languages
English (en)
French (fr)
Other versions
EP1764574B1 (de
Inventor
Naoto Hayashi
Ryoichi Kataoka
Kiyoshi Tanda
Mitsuhiko Akahoshi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valeo Thermal Systems Japan Corp
Original Assignee
Valeo Thermal Systems Japan Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Valeo Thermal Systems Japan Corp filed Critical Valeo Thermal Systems Japan Corp
Publication of EP1764574A1 publication Critical patent/EP1764574A1/de
Application granted granted Critical
Publication of EP1764574B1 publication Critical patent/EP1764574B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
    • F28D1/0308—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • F28D1/0333—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
    • F28D1/0341—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members with U-flow or serpentine-flow inside the conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators

Definitions

  • the present invention relates to a heat exchanger such as an evaporator that is used as a component constituting part of a refrigerating cycle and more specifically, it relates to a structure that may be adopted to achieve better temperature distribution uniformity in the heat exchanging unit.
  • a heat exchanger known in the related art adopts a four-pass structure that includes a plurality of tubes disposed in two rows, i.e., a front row and a rear row along the direction of airflow, through which a coolant flows along an up/down direction, an upper tank unit and a lower tank unit respectively communicating with the upper ends and the lower ends of the tubes and the like (see patent reference literature 1).
  • Patent reference literature 1 Japanese Unexamined Patent Publication No. 2001-74388
  • the liquid coolant flowing through an upper tank unit 100 tends to be distributed in greater quantity to the tubes located on the upstream side along the coolant distribution direction due to gravity
  • the coolant flowing through lower tank units 101 and 102 tends to be distributed in greater quantity to the tubes located on the downstream side along the coolant distribution direction due to inertia, as shown in FIG. 8a.
  • the temperature of the output air will rise markedly over an area E (see FIG. 8b) over which the first pass portion 110 and the fourth pass portion 113 overlap fore and aft along the direction of airflow. This tendency becomes more pronounced when the coolant flows at a low flow rate. Test results indicate that the temperatures in some of the areas rise as high as 10 to 20°C, adversely affecting temperature control in the cabin.
  • an inflow port 9 formed at an evaporator-side intake connector is constricted and the inflow port 9 is set on the upper side along the height of the tanks so as to specifically improve the distribution of the coolant flowing at a low flow rate in the heat exchanger disclosed in patent reference literature 2.
  • this structural feature cannot be utilized to full advantage at a very low flow rate, e.g., at the full destroke setting in an air-conditioning system that employs a variable-displacement compressor.
  • the full capacity setting maximum flow rate
  • another problem occurs in that a great deal of resistance is created at the constriction.
  • An object of the present invention is to provide a heat exchanger with which the distribution of coolant flowing at an extremely low flow rate can be improved, uniformity in the output air temperature can be achieved and the coolant can flow in a sufficient quantity without the heat exchanger structure creating an unwanted resistance at a high flow rate, while minimizing the increase in production costs.
  • a heat exchanger comprising at least a plurality of tubes disposed so as to distribute a coolant along an up/down direction and an upper tank communicating with an upper end portion of a tube group constituted with the tubes, with coolant flowing in through an inflow port located at the upper tank, characterized in that a coolant intake guide passage with an open top is disposed at the inflow port and that the coolant intake guide passage is inserted at the upper tank .
  • the coolant having flowed in through the inflow port in the heat exchanger flows into the coolant intake guide passage, travels down to the lower area inside the heat exchanger and is distributed to the individual tubes. Since the coolant intake guide passage is inserted so as to reach a middle area of the upper tank along the lengthwise direction, the coolant is distributed uniformly. Even when the flow rate is very low, the coolant, flowing through the coolant intake guide passage is allowed to travel to the middle area of the tank. In addition, when the coolant flow rate is set high, the coolant overflows through the open top before it reaches the front end of the coolant intake guide passage and flows into the upper tank. Thus, the coolant does not need to flow against a significant resistance at the coolant intake guide passage and uniform distribution is assured.
  • the inflow port be formed at a heat exchanger-side intake/outlet connector and that the inflow port include a circulator portion and an elongated hole with a rectangular section formed at the circular portion toward the heat exchanger with the elongated hole set higher than the center of the circular portion.
  • the coolant intake guide passage includes an intake pipe-side connector insertion portion, a clamped portion and an open-top flow passage portion. The top surface of the open-top flow passage portion is cut off so as to open up the top thereof.
  • the coolant intake guide passage is mounted by clamping the clamped portion between a heat exchanger-side intake connector and an intake pipe-side connector linked with the heat exchanger-side intake connector. Namely, the coolant intake guide passage clamped between the two connectors is held firmly.
  • the intake pipe-side connector insertion portion of the coolant intake guide passage is flexible so as to allow the coolant intake guide passage to be inserted at the intake pipe with ease.
  • the flexibility of the intake pipe-side connector insertion portion is achieved by forming a slit at a cylindrical portion thereof along the axial direction. It is desirable that the clamped portion at the coolant intake guide passage be formed as a collar and that the open-top flow passage portion be formed as a trough with an open top.
  • the open-top flow passage portion of the coolant intake guide passage be formed at a position offset upward relative to the center of the intake pipe-side connector insertion portion, so as to distribute the coolant further into the tank.
  • the bottom surface of the open-top flow passage portion of the coolant intake guide passage include an inclined surface midway to the front end thereof so as to offset the front end upward, thereby also ensuring that the coolant is allowed to travel further into the tank.
  • a hole may be formed at the bottom surface of the open-top flow passage portion of the coolant intake guide passage. It is desirable that the hole be formed at the inclined surface at the bottom surface, so as to distribute the coolant in an optimal quantity uniformly over the area of the upper tank on the closer side.
  • the coolant intake guide passage disposed in the inflow port is inserted into the tank so as to allow the coolant to flow to the middle area of the tank via the coolant intake guide passage even when the coolant flow rate is very low.
  • the coolant distribution is improved and better uniformity in the temperature distribution is achieved at the heat exchanger according to the present invention.
  • the coolant flow rate is high, the coolant overflows through the open top into the tank before it reaches the front and, thereby achieving another advantage in that the coolant does not need to flow against significant resistance at the coolant intake guide passage.
  • a heat exchanger 1 in FIG. 1, achieved in an embodiment of the present invention, is used as an evaporator constituting part of a refrigerating cycle. It includes tubes 2, fins 3, an upper tank 4, a lower tank 5, endplates 6 and 7, partitioning plates 8, an inflow port 9 and an outflow port 10.
  • the tubes 2 are formed in a flat shape with a hollow space enclosed therein by using a base material the main constituent of which is aluminum. They are disposed over a plurality of rows so as to distribute the coolant along the up/down direction, with tubes disposed in two rows, i.e., a front row and a rear row along the direction of airflow.
  • the tubes 2 include a first tube group 2a of tubes disposed in the row toward the downstream side along the airflow direction and a second tube group 2b of tubes disposed in the row toward the upstream side along the airflow direction.
  • Corrugated fins 3 constituted of a base material the main constituent of which is aluminum are held between the tubes 2, and the end plates 6 and 7 each constituted with a metal plate or the like are fixed at the two ends of the layered assembly of the tubes 2 and the fins 3 along the layering direction.
  • the upper tank 4 communicates with the upper ends of the tubes 2, and includes a first upper tank portion 4a formed on the downstream side along the airflow direction, a second upper tank portion 4b formed on the upstream side along the airflow direction and a communicating passage 4c that communicates between the first upper tank portion 4a and the second upper tank portion 4b at ends on the side opposite from the side where the inflow port 9 and the outflow port 10 are present.
  • the first upper tank portion 4a communicates with the first tube group 2a, whereas the second upper tank portion 4b communicates with the second tube group 2b.
  • the lower tank 5 communicates with the lower ends of the tubes 2, and includes a first lower tank portion 5a formed on the downstream side along the airflow direction and a second lower tank portion 5b formed on the upstream side along the airflow direction, without the first lower tank portion 5a and the second lower tank portion 5b communicating with each other.
  • the first lower tank portion 5a communicates with the first tube group 2a
  • the second lower tank portion 5b communicates with the tube group 2b.
  • the partitioning plates 8 partition the first upper tank portion 4a and the second upper tank portion 4b at substantially central points thereof.
  • the coolant flows through a four-pass flow path, as shown in FIG. 2.
  • the coolant having flowed in through the inflow passage 9 travels from the first upper tank portion 4a -> the first tube group 2a -> a first pass portion 20 constituted with the first lower tank portion 5a and a first lower tank portion 5a' -> a first tube group 2a' -> a second pass portion 21 constituted with a first upper tank portion 4a' and the second upper tank portion 4b -> the second tube group 2b -> a third pass portion 22 constituted with the second lower tank portion 5b and the second lower tank portion 5b' -> a second tube group 2b' -> a fourth pass portion 23 constituted with a second upper tank portion 4b', and then flows out through the outflow port 10.
  • FIG. 3 showing a coolant intake guide passage 25, FIG. 4 showing the intake porn 9 and FIGS. 5 and 6 showing the coolant intake guide passage 25 inserted at the inflow port 9.
  • the inflow port 9 is formed at a heat exchanger-side coolant intake/outlet connector 26 and includes a circular hole 9a formed further toward the closer side and an elongated hole (9b) with a rectangular section formed further inward (toward the heat exchanger).
  • the elongated hole 9b is formed at a position higher than the center of the circular portion 9a.
  • the coolant intake guide passage 25 includes an intake pipe-side connector insertion portion 28, a clamped portion 29 constituted with a collar and an open-top flow passage portion 30.
  • the intake pipe-side connector insertion portion 28 is inserted at an intake pipe-side connector 32 and a plurality of slits 33 are formed along the axial direction at the intake pipe-side connector insertion portion 28, thereby rendering the intake pipe-side connector insertion portion flexible to allow it to be inserted with ease.
  • the clamped portion 29 is a collar with a diameter greater than that at the intake pipe-side connector insertion portion 28. It is clamped between the intake pipe-side connector 32 and the heat exchanger-side coolant intake/outlet connector 26 and is disposed inside the inflow port 9 in this state.
  • the open-top flow passage portion 30, which is a trough-like passage with an open top, includes upright pieces 36 on the two sides of the bottom surface 35 thereof ranging along the lengthwise direction and is offset upward relative to the central point of the intake pipe-side connector insertion portion 28.
  • the bottom surface 35 includes an inclined surface 35a formed midway to the front end thereof, which is made to incline upward, thereby offsetting the front end of the open-top flow passage portion 30 upward.
  • This structure allows the coolant to travel to the middle area inside the first lower tank portion 5a. It is to be noted that since the open-top flow passage portion 30 has an open top, the coolant is allowed to flow into the first lower tank portion 5a over the upright pieces 36 at a high flow rate. In addition, a hole 38 is formed at the bottom surface 35 of the open-top flow passage portion 30 so as to distribute the coolant into the first lower tank portion 5a located on the closer side. Any number of holes 38 may be formed and such holes 38 should be formed at the inclined surface 35a.
  • the coolant intake guide passage 25 is present within the inflow port 9, as described above, the coolant flows in the open-top flow passage portion 30 at the coolant intake guide passage 25, flows in sufficient quantity to the middle area within the first upper tank portion 4a through the first pass portion 20 and is distributed substantially evenly into the first tube group 2a.
  • the range of the area at the first pass portion 20 where the temperature rises higher than the temperature over the other area when the coolant flow rate is low is minimized and even though this area partially overlaps a high temperature area Y at the fourth pass portion 23 fore and aft along the airflow direction and a small high temperature area remains, as shown in FIG. 7b, uniformity is achieved in the temperature distribution in the overall heat exchanger.
  • the air temperature was measured at 30 leeward positions in the heat exchanger 1. At a low coolant flow rate the air temperatures measured at all the measurement points were invariably equal to or less than 5°C when the intake air temperature was 35°C. This is a significant improvement over an example of the related art (see FIG. 8b) in which the temperatures reached 15 to 20° at a plurality of measurement points.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
EP06018890A 2005-09-16 2006-09-08 Wärmetauscher Not-in-force EP1764574B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2005269455A JP4840681B2 (ja) 2005-09-16 2005-09-16 熱交換器

Publications (2)

Publication Number Publication Date
EP1764574A1 true EP1764574A1 (de) 2007-03-21
EP1764574B1 EP1764574B1 (de) 2009-02-25

Family

ID=37684208

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06018890A Not-in-force EP1764574B1 (de) 2005-09-16 2006-09-08 Wärmetauscher

Country Status (4)

Country Link
US (1) US7549466B2 (de)
EP (1) EP1764574B1 (de)
JP (1) JP4840681B2 (de)
DE (1) DE602006005299D1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008085314A2 (en) * 2006-12-19 2008-07-17 E. I. Du Pont De Nemours And Company Dual row heat exchanger and automobile bumper incorporating the same
WO2008140809A3 (en) * 2007-05-11 2009-04-30 Du Pont Method for exchanging heat in a vapor compression heat transfer system and a vapor compression heat transfer system comprising an intermediate heat exchanger with a dual-row evaporator or condenser
EP2447657A3 (de) * 2010-10-28 2015-03-04 Samsung Electronics Co., Ltd. Mehrzonen-Wärmetauscher mit unterteilten Sammelrohren

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US8240367B2 (en) * 2007-06-28 2012-08-14 Exxonmobil Research And Engineering Company Plate heat exchanger port insert and method for alleviating vibrations in a heat exchanger
US7921558B2 (en) * 2008-01-09 2011-04-12 Delphi Technologies, Inc. Non-cylindrical refrigerant conduit and method of making same
US20090173482A1 (en) * 2008-01-09 2009-07-09 Beamer Henry E Distributor tube subassembly
JP5739603B2 (ja) * 2009-01-27 2015-06-24 株式会社小松製作所 熱交換器
CN101788242A (zh) * 2009-03-25 2010-07-28 三花丹佛斯（杭州）微通道换热器有限公司 用于热交换器的制冷剂分配器和热交换器
ES2547868T3 (es) 2009-07-16 2015-10-09 Lockheed Martin Corporation Disposiciones de haces de tubos helicoidales para intercambiadores de calor
WO2011009080A2 (en) 2009-07-17 2011-01-20 Lockheed Martin Corporation Heat exchanger and method for making
US8720536B2 (en) * 2009-09-04 2014-05-13 Modine Manufacturing Company Heat exchanger having flow diverter
US9777971B2 (en) 2009-10-06 2017-10-03 Lockheed Martin Corporation Modular heat exchanger
US9670911B2 (en) * 2010-10-01 2017-06-06 Lockheed Martin Corporation Manifolding arrangement for a modular heat-exchange apparatus
US9388798B2 (en) 2010-10-01 2016-07-12 Lockheed Martin Corporation Modular heat-exchange apparatus
US9581397B2 (en) 2011-12-29 2017-02-28 Mahle International Gmbh Heat exchanger assembly having a distributor tube retainer tab
JP6483409B2 (ja) * 2013-12-26 2019-03-13 カルソニックカンセイ株式会社 熱交換器
JP6458617B2 (ja) * 2015-04-15 2019-01-30 株式会社デンソー 冷媒蒸発器
DE102015210231A1 (de) * 2015-06-03 2016-12-08 Bayerische Motoren Werke Aktiengesellschaft Wärmetauscher für ein Kühlsystem, Kühlsystem sowie Baugruppe
US10551099B2 (en) 2016-02-04 2020-02-04 Mahle International Gmbh Micro-channel evaporator having compartmentalized distribution
US11421939B2 (en) * 2019-09-16 2022-08-23 National Central University Plate heat exchanger with inlet distributor
CN114353387A (zh) * 2021-11-22 2022-04-15 浙江银轮新能源热管理系统有限公司 耐高压的空调换热器

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EP1199534A1 (de) * 2000-10-20 2002-04-24 Mitsubishi Heavy Industries, Ltd. Plattenwärmetauscher
FR2825793A1 (fr) * 2001-06-07 2002-12-13 Valeo Climatisation Evaporateur a plaques presentant un trajet de fuite pour le fluide refrigerant
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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008085314A2 (en) * 2006-12-19 2008-07-17 E. I. Du Pont De Nemours And Company Dual row heat exchanger and automobile bumper incorporating the same
WO2008085314A3 (en) * 2006-12-19 2008-09-25 Du Pont Dual row heat exchanger and automobile bumper incorporating the same
EP4160127A1 (de) * 2007-01-31 2023-04-05 The Chemours Company FC, LLC Dampfkompressionswärmeübertragungssystem
WO2008140809A3 (en) * 2007-05-11 2009-04-30 Du Pont Method for exchanging heat in a vapor compression heat transfer system and a vapor compression heat transfer system comprising an intermediate heat exchanger with a dual-row evaporator or condenser
EP2145150B1 (de) 2007-05-11 2016-04-13 E. I. du Pont de Nemours and Company Verfahren zur wärmetauschung in einem dampfkompressions-wärmeübertragungssystem und dampfkompressions-wärmeübertragungssystem mit einem zwischenwärmetauscher mit einem zweireihigen verdampfer oder kondensator
US11624534B2 (en) 2007-05-11 2023-04-11 The Chemours Company Fc, Llc Method for exchanging heat in vapor compression heat transfer systems and vapor compression heat transfer systems comprising intermediate heat exchangers with dual-row evaporators or condensers
EP2447657A3 (de) * 2010-10-28 2015-03-04 Samsung Electronics Co., Ltd. Mehrzonen-Wärmetauscher mit unterteilten Sammelrohren
US9546824B2 (en) 2010-10-28 2017-01-17 Samsung Electronics Co., Ltd. Heat exchanger

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JP2007078298A (ja) 2007-03-29
US7549466B2 (en) 2009-06-23
DE602006005299D1 (de) 2009-04-09
JP4840681B2 (ja) 2011-12-21
US20070062678A1 (en) 2007-03-22
EP1764574B1 (de) 2009-02-25

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